EP2891795B1 - Hydraulikgetriebe, Windturbinengenerator und Betriebssverfahren dafür - Google Patents

Hydraulikgetriebe, Windturbinengenerator und Betriebssverfahren dafür Download PDF

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Publication number
EP2891795B1
EP2891795B1 EP14188979.0A EP14188979A EP2891795B1 EP 2891795 B1 EP2891795 B1 EP 2891795B1 EP 14188979 A EP14188979 A EP 14188979A EP 2891795 B1 EP2891795 B1 EP 2891795B1
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EP
European Patent Office
Prior art keywords
low pressure
hydraulic
pressure line
pump
line
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Application number
EP14188979.0A
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English (en)
French (fr)
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EP2891795A3 (de
EP2891795A2 (de
Inventor
Kazuhisa Tsutsumi
Michiya Uchida
Hiroyuki Yamaguchi
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Mitsubishi Heavy Industries Ltd
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Mitsubishi Heavy Industries Ltd
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Publication date
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Publication of EP2891795A2 publication Critical patent/EP2891795A2/de
Publication of EP2891795A3 publication Critical patent/EP2891795A3/de
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/38—Control of exclusively fluid gearing
    • F16H61/40—Control of exclusively fluid gearing hydrostatic
    • F16H61/4165—Control of cooling or lubricating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D15/00—Transmission of mechanical power
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D80/00—Details, components or accessories not provided for in groups F03D1/00 - F03D17/00
    • F03D80/70—Bearing or lubricating arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/38—Control of exclusively fluid gearing
    • F16H61/40—Control of exclusively fluid gearing hydrostatic
    • F16H61/4078—Fluid exchange between hydrostatic circuits and external sources or consumers
    • F16H61/4139—Replenishing or scavenging pumps, e.g. auxiliary charge pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/38—Control of exclusively fluid gearing
    • F16H61/40—Control of exclusively fluid gearing hydrostatic
    • F16H61/4192—Detecting malfunction or potential malfunction, e.g. fail safe
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2260/00—Function
    • F05B2260/40—Transmission of power
    • F05B2260/406—Transmission of power through hydraulic systems
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/70—Wind energy
    • Y02E10/72—Wind turbines with rotation axis in wind direction
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
    • Y02P80/00—Climate change mitigation technologies for sector-wide applications
    • Y02P80/10—Efficient use of energy, e.g. using compressed air or pressurized fluid as energy carrier

Definitions

  • the present disclosure relates to a hydraulic transmission including a hydraulic pump and a hydraulic motor, a wind turbine power generating apparatus having the same, and an operation control method of the wind turbine power generating apparatus.
  • renewable energy power generating apparatuses have become widely used, such as a wind turbine power generating apparatus using wind force and a current power generating apparatus using tidal current, river current, or ocean current.
  • a renewable energy power generating apparatus commonly converts kinetic energy of wind, tidal current, ocean current or river current into rotation energy of a rotor, and then the speed of the rotation energy of the rotor is increased by a drive train and the rotation energy is inputted to a generator, thereby generating electric power.
  • Document 1 discloses a wind turbine power generating apparatus using a hydraulic transmission including a hydraulic pump driven by rotation of a rotor and a hydraulic motor connected to a generator.
  • the hydraulic pump and the hydraulic motor are fluidically connected to each other via a high pressure line and a low pressure line.
  • the high-pressure working oil pressurized by the hydraulic pump is supplied to the hydraulic motor through the high pressure oil line, and then the pressure of the working oil is converted into driving force of a generator in the hydraulic motor.
  • the low-pressure working oil discharged from the hydraulic motor is returned to the hydraulic pump through the low pressure oil line.
  • the hydraulic pump includes a plurality of groups of a piston and a cylinder, and a cam for sliding the pistons in the cylinders periodically.
  • Document 2 discloses a hydrostatic-mechanical gear comprising a hydraulic pump being connected via supply and return pipes with a hydraulic motor and forming therewith a high pressure circuit, and a flushing slide valve attached to said supply and return pipes by connecting pipes so that, during operation of said hydrostatic-mechanical gear, heated oil is constantly removed from said high pressure circuit, via a flushing valve and is replaced with cooled oil.
  • Document 3 discloses a renewal energy electric power generating apparatus which transmits the rotational energy of the rotor to a generator via the hydraulic transmission.
  • Document 3 shows a hydraulic transmission according to the preamble of claim 1 and also an operation control method according to the preamble of claim 11.
  • a boost pump is used to supply working oil to the low pressure line connecting the hydraulic pump and the hydraulic motor.
  • the pistons of the hydraulic pump and the hydraulic motor normally reciprocate periodically in the cylinders in accordance with the cam profile.
  • piston jumping may occur.
  • a piston rises off the contacting surface between the piston and the cam surface.
  • the piston jumping occurs, the piston collides with the cam surface when contacting the cam for the next time, which may damage the piston or the cam.
  • a static-pressure pad is disposed at the sliding part between a piston and the cam to supply working oil from the working chambers to the static-pressure pad, the working oil being static-pressure fluid.
  • the oil is not sufficiently supplied to the static-pressure pad, which may damage the static-pressure pad.
  • the hydraulic pump and the hydraulic motor may not be stopped immediately because of inertia, and it may take several tens of seconds before the hydraulic pump and the hydraulic motor stop.
  • the present invention was made in view of the above issues, and an object of at least one embodiment of the present invention is to provide a hydraulic transmission, a wind turbine power generating apparatus, and an operation control method for a wind turbine power generating apparatus which are capable of retarding pressure decrease in a low pressure line when a boost pump abnormally stops, the boost pump being provided for feeding working oil to the low pressure line.
  • a hydraulic transmission according to the present invention is defined by claim 1 and notably includes: a hydraulic pump configured to pressurize working oil; a hydraulic motor configured to be driven by the working oil pressurized by the hydraulic pump; a high pressure line which connects an outlet side of the hydraulic pump and an inlet side of the hydraulic motor; a low pressure line which connects an outlet side of the hydraulic motor and an inlet side of the hydraulic pump; a reservoir tank for storing the working oil, the reservoir tank being connected to the low pressure line; and a boost pump for feeding the working oil stored in the reservoir tank to the low pressure line.
  • the hydraulic transmission is configured such that the working oil is not supplied from the low pressure line to a bearing or a seal of at least one of the hydraulic pump or the hydraulic motor at least during abnormal stop of the boost pump.
  • shutting off the oil supply to the bearings and the seals may not cause damage to the bearings and the seals if the shutoff lasts for only a short period of time such as several tens of seconds after the hydraulic pump and the hydraulic motor begin the stopping operation and before they actually stop.
  • the working oil is supplied to the bearings or the seals of the hydraulic pump and the hydraulic motor from the low pressure line during normal operation of the boost pump, the working oil is not supplied from the low pressure line to at least one of a bearing or a seal of the hydraulic pump or the hydraulic motor when the boost pump abnormally stops due to trouble or blackout.
  • the hydraulic transmission further includes: a first branch line which is branched from the low pressure line and which is communicated with the bearing or the seal of the at least one of the hydraulic pump or the hydraulic motor; and a shutoff valve disposed in the first branch line and configured to control supply of the working oil to the bearing or the seal from the low pressure line via the first branch line.
  • the shutoff valve is configured to be in an open state during normal operation of the boost pump, and to be in a closed state during the abnormal stop of the boost pump so as to shut off the supply of the working oil to the bearing or the seal from the low pressure line via the first branch line.
  • the communicating state between the low pressure line and the bearing or the seal of the hydraulic pump or the hydraulic motor is switchable by opening and closing the shutoff valve disposed in the first branch line.
  • the shutoff valve disposed in the first branch line is in the open state, so that oil is supplied to the bearing or the seal from the low pressure line.
  • the boost pump stops abnormally due to trouble or blackout the shutoff valve is brought into the closed state, so that the oil supply from the low pressure line to the bearing or the seal is shut off.
  • the boost pump stops abnormally due to trouble or blackout
  • the shutoff valve is a pilot check valve configured to be operated by a pressure in the low pressure line serving as a pilot pressure. Also, the pilot check valve is configured to permit a flow to the bearing or the seal from the low pressure line via the first branch line when the pilot pressure is not less than a threshold value P th , and to shut off the flow to the bearing or the seal from the low pressure line via the first branch line when the pilot pressure is less than the threshold value P th .
  • the shutoff valve is brought into the open state so that the oil supply is permitted to the bearing or the seal from the low pressure line via the first branch line.
  • the pressure (pilot pressure) of the low pressure line decreases to less than the threshold value P th , the shutoff valve is brought into the closed state so as to shut off the oil supply to the bearing or the seal from the low pressure line via the first branch line.
  • the threshold value P th is set in assumption of the possible pressure decrease in the low pressure line which may occur when the boost pump abnormally stops, it is possible to appropriately operate the pilot check valve and to retard the pressure decrease in the low pressure line which may occur after the boost pump abnormally stops.
  • the pilot check valve is configured to obtain the pilot pressure from a portion of the low pressure line, the portion being disposed immediately after the boost pump.
  • obtaining the pilot pressure from a portion immediately after the boost pump causes the operation state of the boost pump to be instantly reflected in the pilot-pressure change. Accordingly, it is possible to instantly respond to abnormal stop of the boost pump to bring the pilot check valve (shutoff valve) into the closed state quickly.
  • the hydraulic transmission further includes: an oil supply path provided separately from the low pressure line, the oil supply path connecting the reservoir tank and the bearing or the seal of the at least one of the hydraulic pump or the hydraulic motor; and an oil supply pump disposed in the oil supply path for pumping the working oil to the bearing or the seal of the at least one of the hydraulic pump or the hydraulic motor from the reservoir tank via the oil supply path.
  • the low pressure line is provided separately from the oil supply path, supplying the working oil to the bearing or the seal through the oil supply path during abnormal stop of the boost pump may not cause pressure decrease in the low pressure line.
  • the oil supply pump is configured to be communicable with the hydraulic pump so as to cause the hydraulic pump to perform motoring operation temporarily.
  • the oil supply pump may also function as a pressure oil source for causing the hydraulic pump to perform motoring operation temporarily, in addition to pumping the working oil to the bearing or the seal from the reservoir tank through the oil supply path.
  • a pressure oil source for causing the hydraulic pump to perform motoring operation temporarily, which leads to reduction in size and cost of the hydraulic transmission.
  • the oil supply pump is configured to cause the hydraulic pump to perform motoring operation in order to move a wind turbine rotor of the wind turbine power generating apparatus to a certain position when the wind turbine power generating apparatus having the hydraulic transmission serving as a drive train stops.
  • the hydraulic transmission further includes a low pressure accumulator connected to the low pressure line and configured to reduce pressure fluctuation of the working oil in the low pressure line.
  • the low pressure accumulator is configured to supply the working oil in the low pressure accumulator to the low pressure line during abnormal stop of the boost pump.
  • the working oil having been stored in the low pressure accumulator during operation of the hydraulic transmission is supplied to the low pressure line when the boost pump abnormally stops.
  • the pressure decrease in the low pressure line is suppressed, which makes it possible to further retard the pressure decrease in the low pressure line which may occur after the boost pump abnormally stops.
  • the hydraulic pump or the hydraulic motor is configured to be capable of decreasing rotation speed to at least half of rotation speed in the normal operation in a period of time from when the boost pump abnormally stops to when the pressure of the low pressure line decreases to an initial charge pressure of the low pressure accumulator.
  • the hydraulic transmission further includes: a high pressure accumulator connected to the high pressure line; a bypass flow path which connects the high pressure line and the low pressure line without the hydraulic pump and the hydraulic motor disposed therebetween; and a bypass shutoff valve disposed in the bypass flow path.
  • the bypass shutoff valve is configured to be in a closed state during the normal operation of the boost pump and to be in an open state so as to allow the working oil to flow from the high pressure line to the low pressure line passing through the bypass flow path during the abnormal stop of the boost pump.
  • the bypass shutoff valve is in the closed state during normal operation of the boost pump, so that the flow of the working oil in the bypass flow path is shut off.
  • the bypass shutoff valve is brought into the open state, so that the working oil accumulated in the high pressure accumulator during operation of the hydraulic transmission is supplied to the low pressure line through the bypass flow path.
  • the hydraulic transmission further includes an auxiliary boost pump.
  • the auxiliary boost pump is configured to start operation and suppress pressure decrease in the low pressure line when the boost pump stops abnormally.
  • a wind turbine power generating apparatus includes a wind turbine rotor and a hydraulic transmission connected to the wind turbine rotor.
  • the hydraulic transmission includes: a hydraulic pump configured to be driven by the wind turbine rotor to pressurize working oil; a hydraulic motor configured to be driven by the working oil pressurized by the hydraulic pump; a high pressure line which connects an outlet side of the hydraulic pump and an inlet side of the hydraulic motor; a low pressure line which connects an outlet side of the hydraulic motor and an inlet side of the hydraulic pump; a reservoir tank for storing the working oil, the reservoir tank being connected to the low pressure line; and a boost pump for feeding the working oil stored in the reservoir tank to the low pressure line.
  • the hydraulic transmission is configured such that the working oil is not supplied from the low pressure line to a bearing or a seal of at least one of the hydraulic pump or the hydraulic motor at least during abnormal stop of the boost pump.
  • the working oil in the hydraulic transmission, even though the working oil is supplied to a bearing or a seal of the hydraulic pump or the hydraulic motor from the low pressure line during normal operation of the boost pump, the working oil is not supplied to at least one of the bearing or the seal of the hydraulic pump or the hydraulic motor when the boost pump abnormally stops due to trouble or blackout. Thus, it is possible to retard pressure decrease in the low pressure line, which may occur after the boost pump abnormally stops.
  • the hydraulic pump is configured to be capable of decreasing rotation speed to half of rotation speed in the normal operation within 15 seconds after the boost pump stops abnormally.
  • the hydraulic transmission is configured to maintain the pressure in the low pressure line at not less than a threshold value for a period of time from when the boost pump stops abnormally to at least when the rotation speed of the hydraulic pump decreases to half of the rotation speed in the normal operation.
  • the pressure decrease in the low pressure line is suppressed at least until the rotation speed of the hydraulic pump decreases by half. That is, it is suppressed during a period of time in which the rotation speed of the hydraulic pump is relatively high and has a large influence on the components of the hydraulic transmission such as the pistons and the static-pressure pad caused by piston jumping or insufficient oil supply. As a result, it is possible to effectively prevent damage to components of the hydraulic transmission such as the pistons and the static-pressure pad due to pressure decrease in the low pressure line.
  • the hydraulic motor is configured to be capable of decreasing rotation speed to half of rotation speed in the normal operation within 60 seconds after the boost pump stops abnormally.
  • the hydraulic transmission is configured to maintain the pressure in the low pressure line at not less than a threshold value for a period of time from when the boost pump stops abnormally to at least when the rotation speed of the hydraulic motor decreases to half of the rotation speed in the normal operation.
  • the pressure decrease in the low pressure line is suppressed at least until the rotation speed of the hydraulic motor decreases by half. That is, it is suppressed during a period of time in which the rotation speed of the hydraulic motor is relatively high and has a large influence on the components of the hydraulic transmission such as the pistons and the static-pressure pad caused by piston jumping or insufficient oil supply. As a result, it is possible to effectively prevent damage to components of the hydraulic transmission such as the pistons and the static-pressure pad due to pressure decrease in the low pressure line.
  • An operation control method for a wind turbine power generating apparatus is for a wind turbine power generating apparatus including a wind turbine rotor and a hydraulic transmission connected to the wind turbine rotor.
  • the hydraulic transmission includes: a hydraulic pump configured to be driven by the wind turbine rotor to pressurize working oil; a hydraulic motor configured to be driven by the working oil pressurized by the hydraulic pump; a high pressure line which connects an outlet side of the hydraulic pump and an inlet side of the hydraulic motor; a low pressure line which connects an outlet side of the hydraulic motor and an inlet side of the hydraulic pump; a reservoir tank for storing the working oil, the reservoir tank being connected to the low pressure line; and a boost pump for feeding the working oil stored in the reservoir tank to the low pressure line.
  • the operation control method includes: a detecting step of detecting abnormal stop of the boost pump; and a speed-decreasing step of decreasing rotation speed of the hydraulic pump or the hydraulic motor while the working oil is not supplied from the low pressure line to a bearing or a seal of at least one of the hydraulic pump or the hydraulic motor, after detecting the abnormal stop of the boost pump in the detecting step.
  • the working oil in the hydraulic transmission, even though the working oil is supplied to the bearing or the seal of the hydraulic pump or the hydraulic motor from the low pressure line during normal operation of the boost pump, the working oil is not supplied to at least one of the bearing or the seal of the hydraulic pump or the hydraulic motor when the boost pump abnormally stops due to trouble or blackout. Thus, it is possible to retard pressure decrease in the low pressure line, which may occur after the boost pump abnormally stops.
  • the speed of the hydraulic pump or the hydraulic motor is decreased in a state where the working oil is not supplied from the low pressure line to the bearing or the seal of the hydraulic pump or the hydraulic motor, i.e., in a state where the pressure decrease in the low pressure line is suppressed.
  • displacement of each of the hydraulic pump and the hydraulic motor is set to a minimum value while controlling pitch angle of the wind turbine rotor so that aerodynamic braking force is applied to the wind turbine rotor.
  • the pitch angle of the wind turbine rotor is controlled so as to apply aerodynamic braking force to the wind turbine rotor, which makes it possible to reduce the speed of the hydraulic pump. Further, setting the displacement of each of the hydraulic pump and the hydraulic motor to a minimum value makes it possible to reduce the speed of the hydraulic pump and the hydraulic motor.
  • FIGs. 1 to 5 are each a schematic diagram of a wind turbine power generating apparatus having a hydraulic transmission according to one embodiment.
  • the wind turbine power generating apparatus 1 mainly includes a wind turbine rotor 3 which rotates upon receiving wind, a hydraulic transmission 2 which increases rotation speed of the wind turbine rotor 3, and a generator 16 which generates electric power.
  • the wind turbine rotor 3 includes at least one blade 4, a hub 5 to which the blades 4 are attached, and a rotational shaft 6 coupled to the hub 5. With this configuration, the whole wind turbine rotor 3 rotates by the wind force received by the blades 4, and the rotation is inputted from the rotational shaft 6 to the hydraulic transmission 2. The rotation inputted from the rotational shaft 6 is accelerated by the hydraulic transmission 2, and then the rotation is transmitted to the generator 16 via a rotation shaft 9.
  • the hydraulic transmission 2 includes a hydraulic pump 8 of a variable displacement type, a hydraulic motor 10 of a variable displacement type, a high pressure line 12 and a low pressure line 14 disposed between the hydraulic pump 8 and the hydraulic motor 10, a reservoir tank 18 for storing working oil, and a boost pump 22 for feeding working oil stored in the reservoir tank to the low pressure line 14.
  • the hydraulic pump 8 and the hydraulic motor 10 may be of a variable displacement type which can adjust the displacement.
  • the hydraulic pump 8 is driven by rotation of the wind turbine rotor 3 to pressurize of the working oil.
  • the hydraulic motor 10 is configured to be driven by the working oil pressurized by the hydraulic pump 8.
  • the outlet side of the hydraulic pump 8 is connected to the inlet side of the hydraulic motor 10 through the high pressure line 12, while the inlet side of the hydraulic pump 8 is connected to the outlet side of the hydraulic motor 10 through the low pressure line 14.
  • the working oil (high pressure oil) discharged from the hydraulic pump 8 flows into the hydraulic motor 10 through the high pressure line 12, and then drives the hydraulic motor 10.
  • the working oil (low pressure oil) having performed work in the hydraulic motor 10 flows into the hydraulic pump 8 through the low pressure line 14, has its pressure increased by the hydraulic pump 8, and then flows into the hydraulic motor 10 again through the high pressure line 12.
  • the low pressure line 14 as illustrated in FIG. 1 includes a main-stream line 14A connecting the outlet side of the hydraulic motor 10 and the inlet side of the hydraulic pump 8, and a supplementary line 14B branched from the main-stream line 14A.
  • a reservoir tank 18 is connected to the main-stream line 14A via the supplementary line 14B.
  • the reservoir tank 18 stores supplementary working oil.
  • This working oil stored in the reservoir tank 18 is pumped up by the boost pump 22 disposed in the supplementary line 14B and then supplied to the low pressure line 14 (main-stream line 14A).
  • impurity substances included in the working oil supplied to the low pressure line 14 (main-stream line 14A) may be removed by an oil filter (not illustrated) disposed in the supplementary line 14B.
  • Supplying the supplementary working oil to the low pressure line 14 (main-stream line 14A) makes it possible to maintain the amount of working oil circulating in the hydraulic transmission 2 even in case of leakage of the working oil.
  • a return line 24 is disposed between the main-stream line 14A and the reservoir tank 18, and a relief valve 26 is disposed in the return line 24.
  • a pressure sensor 29 for measuring pressure in the low pressure line 14 may be disposed at the downstream side of the boost pump 22 in the low pressure line 14.
  • a pressure sensor 29 is disposed at the downstream side of the boost pump 22 in the supplementary line 14B, so that the pressure sensor 29 can measure the pressure in the supplementary line 14B.
  • the hydraulic transmission 2 is configured such that, during normal operation, oil for lubrication or cooling is supplied to the bearing and/or seal (oil-supply target part) of the hydraulic pump 8 and/or the hydraulic motor 10.
  • the hydraulic transmission 2 includes a first branch line 32 branched from the low pressure line 14 to communicate with an oil-supply target part of the hydraulic pump 8.
  • the first branch line 32 includes a shutoff valve 34 for controlling the supply of the working oil supplied from the low pressure line 14 to the bearing via the first branch line 32.
  • the communicating state between the bearing of the hydraulic pump 8 and the low pressure line 14 via the first branch line 32 is switchable by opening and closing the shutoff valve 34.
  • the shutoff valve 34 is in an open state, so that the oil is supplied to the bearing of the hydraulic pump 8 from the low pressure line 14 via the first branch line 32.
  • the hydraulic transmission 2 includes an oil supply path 38 provided separately from the low pressure line 14, the oil supply path 38 connecting the bearing of the hydraulic pump 8 and the reservoir tank 18.
  • the oil supply path 38 includes an oil supply pump 36 for pumping the working oil to the bearing of the hydraulic pump 8 from the reservoir tank 18 through the oil supply path 38.
  • the hydraulic transmission 2 is configured such that the working oil is not supplied to the bearing of the hydraulic pump 8 from the low pressure line 14 during abnormal stop of the boost pump 22.
  • the shutoff valve 34 is in a closed state during abnormal stop of the boost pump 22, so as to shut off the supply of the working oil to the bearing of the hydraulic pump 8 from the low pressure line 14 via the first branch line 32.
  • the shutoff valve 34 is in a closed state during abnormal stop of the boost pump 22, so as to shut off the supply of the working oil to the bearing of the hydraulic pump 8 from the low pressure line 14 via the first branch line 32.
  • providing the oil supply path 38 and the oil supply pump 36 makes it possible to supply the working oil for lubrication and cooling to the bearing of the hydraulic pump 8 without passing through the low pressure line 14.
  • the oil for lubrication and cooling is not supplied to the bearing of the hydraulic pump 8 through the low pressure line 14 during abnormal stop of the boost pump 22.
  • supplying the working oil to the bearing of the hydraulic pump 8 through the oil supply path 38 during abnormal stop of the boost pump 22 does not by itself cause the pressure decrease in the low pressure line 14.
  • even if the boost pump 22 stops abnormally it is possible to prevent damage to the bearing of the hydraulic pump 8 by supplying the oil for lubrication and cooling without passing through the low pressure line 14.
  • a shutoff-valve control part 39 controls the shutoff valve 34 to be open and closed on the basis of detection signals sent from a pressure sensor 29 disposed at the downstream side of the boost pump 22 in the low pressure line 14.
  • the shutoff-valve control part 39 is configured to control the shutoff valve 34 to be open and closed so that the flow from the low pressure line 14 to the oil supply target part of the hydraulic pump 8 via the first branch line 32 is permitted when pressure P in the low pressure line 14 detected by the pressure sensor 29 is not less than the threshold value, and so that the flow from the low pressure line 14 to the oil supply target part of the hydraulic pump 8 via the first branch line 32 is shut off when the pressure P is less than the threshold value.
  • the threshold value here of the pressure P is a reference for the opening and closing control of the shutoff valve 34 and set in anticipation of the possible pressure decrease in the low pressure line 14 during abnormal stop of the boost pump 22. That is, the threshold value of the pressure P is set at such a value that enables discrimination between normal operation and abnormal stop of the boost pump 22.
  • the shutoff-valve control part 39 controls opening and closing operation of the shutoff valve 34 based on the detection results of the pressure sensor 29 as described above.
  • the shutoff valve 34 is closed in response to the decrease in the pressure P after the boost pump 22 abnormally stops, which makes it possible to prevent leakage of the working oil to the oil supply target part from the low pressure line 14 via the first branch line 32.
  • the pressure sensor 29 is configured to measure pressure P at a portion from the low pressure line 14 immediately after the boost pump 22, i.e., pressure P between the boost pump 22 and the meeting point where the main-stream line 14A merges with the supplementary line 14B in which the boost pump 22 is disposed.
  • the pilot pressure is obtained from a portion immediately after the boost pump 22.
  • the operation state of the boost pump 22 is instantly reflected in the measurement result of the pressure sensor 29.
  • the shutoff valve 34 is a pilot check valve 35 configured to operate with the pressure in the low pressure line 14 as its pilot pressure.
  • the pilot check valve 35 is configured to permit the flow from the low pressure line 14 to the oil supply target part of the hydraulic pump 8 via the first branch line 32 when the pilot pressure is not less than the threshold value P th , and to shut off the flow from the low pressure line 14 to the oil supply target part of the hydraulic pump 8 via the first branch line 32 when the pilot pressure is less than the threshold value P th .
  • the threshold value P th of the pilot pressure is set in anticipation of the possible pressure decrease of the low pressure line 14 which may occur during abnormal stop of the boost pump 22. That is, the threshold value P th is set such that the pilot pressure (pressure in the low pressure line) is not less than P th during normal operation of the boost pump 22 and the pilot pressure is less than P th during abnormal stop of the boost pump 22.
  • the pilot pressure is not less than the threshold value P th and the pilot check valve is in the open state during normal operation of the boost pump 22, and thus the oil is supplied to the oil supply target part of the hydraulic pump 8 from the low pressure line 14 via the first branch line 32.
  • the pilot pressure pressure in the low pressure line
  • the pilot check valve 35 is brought into the closed state, and thus the supply of the working oil to the oil supply target part of the hydraulic pump 8 from the low pressure line 14 via the first branch line 32 is shut off.
  • the pilot check valve 35 obtains its pilot pressure from a portion from the low pressure line 14 immediately after the boost pump 22, i.e., from a portion between the boost pump 22 and the meeting point where the main-stream line 14A merges with the supplementary line 14B in which the boost pump 22 is disposed.
  • the pilot pressure is obtained from a portion immediately after the boost pump 22.
  • the operation state of the boost pump 22 is instantly reflected in the change in the pilot pressure.
  • the pilot check valve 35 shutoff valve 34
  • the pilot check valve 35 may obtain its pilot pressure from a portion between the boost pump 22 and the non-return valve.
  • the pilot check valve 35 may obtain its pilot pressure from a portion between the boost pump 22 and the oil filter.
  • the oil supply path 38 and the oil supply pump 36 for supplying the working oil to the oil supply target part may be configured to be usable as an oil flow path and a pressure oil source, respectively, for causing the hydraulic pump 8 to carry out motoring operation (motoring) temporarily.
  • the oil supply path 38 is configured capable of bringing the reservoir tank 18 into communication with the hydraulic chambers of the hydraulic pump 8
  • the oil supply pump 36 may be configured capable of supplying pressurized oil to the hydraulic chambers of the hydraulic pump through the oil supply path 38.
  • Motoring is carried out by the hydraulic pump 8, for instance, when moving the wind turbine rotor 3 to a certain angular position for maintenance of the wind turbine power generating apparatus 1, or when moving the rotation shaft of the hydraulic pump 8 to a certain angular position for maintenance of the hydraulic pump 8.
  • the oil supply pump 36 it is possible to make the oil supply pump 36 to function as a pressurized oil source for causing the hydraulic pump 8 to temporarily perform motoring operation, in addition to pumping the working oil to the oil supply target part of the hydraulic pump 8 from the reservoir tank 18 through the oil supply path 38.
  • the hydraulic transmission 2 illustrated in FIG. 4 includes a low pressure accumulator 42 connected to the low pressure line 14 for suppressing pressure fluctuation of the working oil in the low pressure line 14.
  • the low pressure accumulator 42 is configured to supply the working oil accumulated in the low pressure accumulator 42 to the low pressure line 14 during abnormal stop of the boost pump 22.
  • the low pressure accumulator 42 may be, for instance, of a piston type or a bladder type in which a deformable bladder is used to separate gas and the working oil from each other.
  • an initial charge pressure of the low pressure accumulator 42 is set such that the working oil is accumulated in the low pressure accumulator 42 while the hydraulic transmission 2 is operating normally. Then, when the boost pump 22 abnormally stops, the working oil accumulated in the low pressure accumulator 42 is supplied to the low pressure line 14 as the pressure in the low pressure line 14 begins to decrease, and all this time the pressure in the low pressure line 14 is maintained close to the initial charge pressure. Accordingly, the pressure decrease in the low pressure line 14 which may occur after the boost pump 22 abnormally stops is even more retarded.
  • the exemplary embodiment illustrated in FIG.4 similarly to the embodiments illustrated in FIGs. 1 and 2 , includes halting the supply of the working oil from the low pressure line 14 to the oil supply target part of the hydraulic pump 8 during abnormal stop of the boost pump 22 via the first branch line 32 and the shutoff valve 34, the working oil may be supplied to the oil supply target part from the oil supply pump 36 regardless of the operation state of the boost pump 22, similarly to the embodiment illustrated in FIG. 3 .
  • the capacity of the low pressure accumulator 42 may be set so that the working oil can be supplied to the low pressure line 14 long enough to suppress the damage to the pistons and the static-pressure pad due to piston jumping or insufficient oil supply after the boost pump 22 abnormally stops.
  • the capacity of the low pressure accumulator 42 so as to enable supplying the working oil to the low pressure line 14 from the low pressure accumulator 42 until the rotation speed of the hydraulic pump 8 and the hydraulic motor 10 becomes such that it is possible to suppress the damage to the pistons and the static-pressure pad due to piston jumping or insufficient oil supply.
  • the hydraulic pump 8 is configured such that the rotation speed can decrease at least to half the rotation speed in the normal operation within a period of time from when the boost pump 22 abnormally stops to when the pressure in the low pressure line 14 decreases to the initial charge pressure of the low pressure accumulator 42.
  • the low pressure accumulator 42 has such a capacity that the working oil can be supplied to the low pressure line 14 at least until the rotation speed of the hydraulic pump 8 falls by half from the rotation speed in the normal operation.
  • the hydraulic transmission 2 further includes a high pressure accumulator 44 connected to the high pressure line 12, and a bypass flow path 46 connecting the high pressure line 12 and the low pressure line 14 without the hydraulic pump 8 and the hydraulic motor 10 being interposed.
  • a bypass shutoff valve 48 is disposed in the bypass flow path 46.
  • the bypass shutoff valve 48 is configured to be in a closed state during normal operation of the boost pump 22 and to be in an open state during abnormal stop of the boost pump 22 so as to allow the working oil to flow from the high pressure line 12 to the low pressure line 14 through the bypass flow path 46.
  • the bypass shutoff valve 48 may be an electromagnetic valve or a pilot check valve which is closed in response to pressure decrease in the low pressure line 14.
  • the bypass shutoff valve 48 may be an electromagnetic valve which is controlled to open or close on the basis of measurement results of the pressure sensor 29 (see FIG. 1 ) or a pilot check valve which operates with the pressure of the low pressure line 14 as its pilot pressure.
  • the high pressure accumulator 44 may be of a piston type or a bladder type in which a deformable bladder is used to separate gas and the working oil from each other.
  • a bypass flow path 52 that bypasses the hydraulic motor 10 may be disposed between the high pressure line 12 and the low pressure line 14, the bypass flow path 52 including a relief valve 54 which maintains the pressure of the working oil in the high pressure line 12 at the setting pressure or lower.
  • the high pressure accumulator 44 is configured to accumulate the extra portion of the high pressure oil (working oil) discharged to the high pressure line 12 from the hydraulic pump 8 during normal operation of the hydraulic transmission 2.
  • the relief valve 54 automatically opens. As a result, it is possible to feed the high pressure oil to the low pressure line 14 through the bypass flow path 52 to maintain the pressure of the high pressure line 12 within an appropriate range when the pressure in the high pressure line 12 has increased excessively during normal operation of the hydraulic transmission 2.
  • bypass flow path 46 and the bypass shutoff valve 48 are disposed between the high pressure line 12 and the low pressure line 14 separately from the bypass flow path 52 and the relief valve 54.
  • the bypass shutoff valve 48 is in a closed state during normal operation of the boost pump 22, so as to shut off the flow of the working oil in the bypass flow path 46.
  • the bypass shutoff valve 48 is brought into an open state, so that the working oil accumulated in the high pressure accumulator 44 during operation of the hydraulic transmission 2 is supplied to the low pressure line 14 passing through the bypass flow path 46.
  • the pressure decrease in the low pressure line 14 is suppressed. Accordingly, it is possible to further retard the pressure decrease in the low pressure line 14 which may occur after the boost pump 22 abnormally stops.
  • a high pressure accumulator of a wind turbine power generating apparatus normally has larger capacity than that of a low pressure accumulator due to a function of so called Low Voltage Ride-Through (LVRT) for maintaining the level of the output without disconnecting, as far as possible, a wind turbine power generating apparatus from a utility grid to which the wind turbine power generating apparatus is connected, even if the electric voltage of the utility grid decreases. Therefore, it is possible to maintain the pressure in the low pressure line 14 for a relatively long time by providing the bypass flow path 46 and the bypass shutoff valve 48 between the high pressure line 12 and the low pressure line 14 and bringing this bypass shutoff valve 48 into an open state when the boost pump 22 abnormally stops.
  • LVRT Low Voltage Ride-Through
  • FIG. 6 is a flowchart of an operation control method for a wind turbine power generating apparatus according to one embodiment.
  • step S2 abnormal stop of the boost pump 22 is detected (step S2). If abnormal stop of the boost pump 22 is not detected in step S2 (determination result "NO” in step S2), step 2 is repeated. On the other hand, if abnormal stop of the boost pump 22 is detected in step S2 (determination result "YES” in step S2), the method proceeds to step S4.
  • abnormal stop of the boost pump 22 may be detected for the wind turbine power generating apparatus 1 having configuration illustrated in FIG. 1 , for instance, by comparing the measurement value of pressure P in the low pressure line 14 (supplementary line 14B) obtained by the pressure sensor 29 with a threshold value.
  • abnormal stop of the boost pump 22 may be detected by comparing the pressure in the low pressure line 14 (supplementary line 14B) used as the pilot pressure for the pilot check valve 35 with the setting pressure (threshold value P th ) of the pilot check valve 35.
  • step S4 supplying the working oil from the low pressure line 14 to the oil supply target part of at least one of the hydraulic pump 8 or the hydraulic motor 10 is halted.
  • the shutoff valve 34 is closed on the basis of the measurement results of the pressure sensor 29 under control of the shutoff valve control part 39, so that the supply of the working oil from the low pressure line 14 to the oil supply target part of the hydraulic pump 8 via the first branch line 32 is stopped.
  • the pilot check valve 35 is closed in response to the pilot pressure (pressure of the low pressure line 14) becoming lower than the threshold value P th , so as to stop supplying the working oil from the low pressure line 14 to the oil supply target part of the hydraulic pump 8 via the first branch line 32.
  • step 6 the rotation speed of the hydraulic pump 8 and the hydraulic motor 10 is decreased while halting the supply of the working oil from the low pressure line 14 to the oil supply target part.
  • the pitch drive mechanism 60 illustrated in FIG. 7 is used to control the pitch angle of the wind turbine rotor 3, thereby applying aerodynamic braking force to the wind turbine rotor 3.
  • FIG. 7 is a diagram of an exemplary configuration of a pitch drive mechanism.
  • the pitch drive mechanism 60 illustrated in FIG. 7 includes a hydraulic cylinder 62, a servo valve 64, a hydraulic pressure source 66, and an accumulator 68, and is accommodated in a hub which also accommodates, for instance, the hydraulic transmission 2 of the wind turbine power generating apparatus 1 illustrated in FIG. 1 .
  • the servo valve 64 adjusts the amount of the high pressure oil supplied to the hydraulic cylinder 62 under control of the pitch control part 33 so that the pitch angle of the blades 4 becomes a desired value, the high pressure oil including high pressure oil generated by the hydraulic pressure source 66 and high pressure oil accumulated in the accumulator 68.
  • the rotation speed of the hydraulic pump 8 is decreased by controlling the pitch drive mechanism 60 by the pitch control part 33 to adjust the pitch angle of the blades 4 so as to decrease the speed of the rotor 3.
  • the displacement of the hydraulic pump 8 and the hydraulic motor 10 may be minimized so as to decrease the rotation speed of the hydraulic pump 8 and the hydraulic motor 10.
  • FIG. 8 is a diagram of an exemplary configuration of a hydraulic pump.
  • the hydraulic pump 8 includes a plurality of working chambers 53 each of which is formed by a cylinder 50 and a piston 52, a cam 54 having a cam curved surface engaging with the pistons 52, and a high pressure valve 56 and a low pressure valve 58 disposed corresponding to each working chamber 53.
  • each piston 52 includes a piston body 52A which slides in a corresponding cylinder 50, and a piston roller 52B attached to the piston body 52A and engaged with the cam curved surface of the cam 54 in view of smoothly operating the piston 52 in accordance with the cam curved surface of the cam 54.
  • the cam 54 is mounted to the outer circumferential face of the rotational shaft 6 via a cam attachment base 55.
  • a high pressure valve 56 is disposed in a high pressure communication path 57 provided between each working chamber 53 and the high pressure line 12.
  • a low pressure valve 58 is disposed in a low pressure communication path 59 between each working chamber 53 and the low pressure line 14. The timing for opening and closing the high pressure valves 56 and the low pressure valves 58 is controlled by the pump control part 37.
  • the pump control part 37 may control the high pressure valves 56 and the low pressure valves 58 so that all working chambers 53 of the hydraulic pump 8 become non-active chambers.
  • the pump control part 37 controls the valves in each working chamber 53 to maintain a state in which the high pressure valve 56 is closed and the low pressure valve 58 is open in a cycle so that pressure of the working oil is not increased. In a single cycle, the piston 52 rises from the bottom dead center, reaches the top dead center, and then returns to the bottom dead center again.
  • step S6 load current is continuously transmitted to an armature of the generator 16 so that electromagnetic torque is generated in the generator 16 even after the boost pump 22 abnormally stops.
  • the boost pump 22 abnormally stops, it is possible to quickly decrease the speed of the rotation shaft of the hydraulic motor 10 by applying the electromagnetic torque of the generator 16 to the rotation shaft of the hydraulic motor 10 while minimizing the displacement to reduce mechanical energy inputted into the rotation shaft of the hydraulic motor 10.
  • an abnormal event occurring at the grid may result in outage of the electric supply to the boost pump 22, causing abnormal stop of the boost pump 22.
  • using a permanent magnet generator as an exciter for a synchronous generator being the generator 16 makes it possible to feed load current continuously to the armature of the generator 16 even if an abnormal event occurs in the grid. Thus, it is possible to maintain the electromagnetic torque of the generator 16.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Wind Motors (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Auxiliary Drives, Propulsion Controls, And Safety Devices (AREA)
  • Control Of Transmission Device (AREA)

Claims (12)

  1. Hydraulisches Getriebe (2), umfassend:
    eine Hydraulikpumpe (8), die dafür konfiguriert ist, Arbeitsöl mit Druck zu beaufschlagen,
    einen Hydraulikmotor (10), der dafür konfiguriert ist, durch das durch die Hydraulikpumpe (8) mit Druck beaufschlagte Arbeitsöl angetrieben zu werden,
    eine Hochdruckleitung (12), die eine Auslassseite der Hydraulikpumpe (8) und eine Einlassseite des Hydraulikmotors (10) verbindet,
    eine Niederdruckleitung (14), die eine Auslassseite des Hydraulikmotors (10) und eine Einlassseite der Hydraulikpumpe (8) verbindet,
    einen Vorratstank (18) zum Speichern des Arbeitsöls, wobei der Vorratstank (18) mit der Niederdruckleitung (14) verbunden ist, und
    eine Verstärkerpumpe (22) zum Zuführen des in dem Vorratstank (18) gespeicherten Arbeitsöls zu der Niederdruckleitung (14),
    eine erste Abzweigleitung (32), die von der Niederdruckleitung (14) abzweigt und mit einem Lager oder einer Dichtung von wenigstens einem von der Hydraulikpumpe (8) und dem Hydraulikmotor (10) in Strömungsverbindung steht, und
    dadurch gekennzeichnet, dass das hydraulische Getriebe (2) ferner ein Absperrventil (34) umfasst, das in der ersten Abzweigleitung (32) angeordnet ist und dafür konfiguriert ist, die Zufuhr des Arbeitsöls zu dem Lager oder der Dichtung von der Niederdruckleitung (14) über die erste Abzweigleitung (32) zu steuern,
    und dadurch, dass das hydraulische Getriebe (2) so konfiguriert ist, dass das Arbeitsöl zumindest während eines abnormalen Stopps der Verstärkerpumpe (22) nicht von der Niederdruckleitung (14) zu dem Lager oder der Dichtung des wenigstens einem von der Hydraulikpumpe (8) und dem Hydraulikmotor (10) zugeführt wird, und
    das Absperrventil (34) dafür konfiguriert ist, während des normalen Betriebes der Verstärkerpumpe (22) in einem offenen Zustand zu sein und während des abnormalen Stopps der Verstärkerpumpe (22) in einem geschlossenen Zustand zu sein, so dass die Zufuhr des Arbeitsöls zu dem Lager oder der Dichtung von der Niederdruckleitung (14) über die erste Abzweigleitung (32) gesperrt wird.
  2. Hydraulisches Getriebe (2) nach Anspruch 1,
    wobei das Absperrventil (34) ein Pilot-Rückschlagventil ist, das dafür konfiguriert ist, durch einen Druck in der Niederdruckleitung (14), der als ein Pilotdruck dient, betätigt zu werden, und
    wobei das Pilot-Rückschlagventil dafür konfiguriert ist, einen Fluss zu dem Lager oder der Dichtung von der Niederdruckleitung (14) über die erste Abzweigleitung (32) zu gestatten, wenn der Pilotdruck nicht unter einem Schwellenwert Pth liegt, und das Fließen zu dem Lager oder der Dichtung von der Niederdruckleitung (14) über die erste Abzweigleitung (32) abzusperren, wenn der Pilotdruck unter dem Schwellenwert Pth liegt.
  3. Hydraulisches Getriebe (2) nach Anspruch 2,
    wobei das Pilot-Rückschlagventil dafür konfiguriert ist, den Pilotdruck von einem Abschnitt der Niederdruckleitung (14) zu erhalten, wobei der Abschnitt unmittelbar nach der Verstärkerpumpe (22) angeordnet ist.
  4. Hydraulisches Getriebe (2) nach einem der Ansprüche 1 bis 3, ferner umfassend
    einen Niederdruckakkumulator, der mit der Niederdruckleitung (14) verbunden ist und dafür konfiguriert ist, Druckschwankungen des Arbeitsöls in der Niederdruckleitung (14) zu reduzieren,
    wobei der Niederdruckakkumulator dafür konfiguriert ist, das Arbeitsöl in dem Niederdruckakkumulator während des abnormalen Stopps der Verstärkerpumpe (22) der Niederdruckleitung (14) zuzuführen.
  5. Hydraulisches Getriebe (2) nach Anspruch 4,
    wobei die Hydraulikpumpe (8) oder der Hydraulikmotor (10) dafür konfiguriert ist, in einem Zeitraum ab dem Moment, wo die Verstärkerpumpe (22) abnormal stoppt, bis zu dem Moment, wo der Druck der Niederdruckleitung (14) auf einen Anfangsladedruck des Niederdruckakkumulators abnimmt, die Drehzahl auf mindestens die Hälfte der Drehzahl des normalen Betriebes senken zu können.
  6. Hydraulisches Getriebe (2) nach einem der Ansprüche 1 bis 5, ferner umfassend:
    einen Hochdruckakkumulator, der mit der Hochdruckleitung (12) verbunden ist,
    einen Umgehungsströmungspfad, der die Hochdruckleitung (12) und die Niederdruckleitung (14) verbindet, ohne dass die Hydraulikpumpe (8) und der Hydraulikmotor (10) dazwischen angeordnet sind, und
    ein Umgehungsabsperrventil (48), das in dem Umgehungsströmungspfad angeordnet ist,
    wobei das Umgehungsabsperrventil (48) dafür konfiguriert ist, während des normalen Betriebes der Verstärkerpumpe (22) in einem geschlossenen Zustand zu sein und während des abnormalen Stopps der Verstärkerpumpe (22) in einem offenen Zustand zu sein, damit das Arbeitsöl von der Hochdruckleitung (12) zu der Niederdruckleitung (14) strömen und dabei den Umgehungsströmungspfad passieren kann.
  7. Hydraulisches Getriebe (2) nach einem der Ansprüche 1 bis 6, ferner umfassend
    eine Zusatzverstärkerpumpe,
    wobei die Zusatzverstärkerpumpe dafür konfiguriert ist, den Betrieb zu starten und eine Druckverringerung in der Niederdruckleitung (14) zu verringern, wenn die Verstärkerpumpe (22) abnormal stoppt.
  8. Windturbinen-Energieerzeugungsvorrichtung (1), ferner umfassend
    einen Windturbinenrotor (3) und ein hydraulisches Getriebe (2), das mit dem Windturbinenrotor (3) verbunden ist,
    wobei das hydraulische Getriebe (2) das hydraulische Getriebe nach Anspruch 1 ist, und wobei die Hydraulikpumpe (8) des hydraulischen Getriebes (2) dafür konfiguriert ist, durch den Windturbinenrotor angetrieben zu werden.
  9. Windturbinen-Energieerzeugungsvorrichtung (1) nach Anspruch 8,
    wobei die Hydraulikpumpe (8) dafür konfiguriert ist, die Drehzahl innerhalb von 15 Sekunden, nachdem die Verstärkerpumpe (22) abnormal gestoppt hat, auf die halbe Drehzahl des normalen Betriebes senken zu können, und
    wobei das hydraulische Getriebe (2) dafür konfiguriert ist, einen Druck in der Niederdruckleitung (14) über einen Zeitraum ab dem Moment, wo die Verstärkerpumpe (22) abnormal stoppt, bis zu mindestens dem Moment, wo die Drehzahl der Hydraulikpumpe (8) auf die Hälfte der Drehzahl des normalen Betriebes gesunken ist, auf nicht weniger als einem Schwellenwert zu halten.
  10. Windturbinen-Energieerzeugungsvorrichtung (1) nach Anspruch 8 oder 9, wobei der Hydraulikmotor (10) dafür konfiguriert ist, die Drehzahl innerhalb von 60 Sekunden, nachdem die Verstärkerpumpe (22) abnormal gestoppt hat, auf die Hälfte der Drehzahl des normalen Betriebes verringern zu können, und
    wobei das hydraulische Getriebe dafür konfiguriert ist, einen Druck in der Niederdruckleitung (14) über einen Zeitraum ab dem Moment, wo die Verstärkerpumpe (22) abnormal stoppt, bis zu mindestens dem Moment, wo die Drehzahl des Hydraulikmotors (10) auf die Hälfte der Drehzahl des normalen Betriebes gesunken ist, auf nicht weniger als einem Schwellenwert zu halten.
  11. Betriebssteuerungsverfahren für eine Windturbinen-Energieerzeugungsvorrichtung (1) nach Anspruch 8, und dadurch gekennzeichnet, dass es umfasst:
    einen Detektionsschritt des Detektierens eines abnormalen Stopps der Verstärkerpumpe (22) und
    einen Drehzahlverringerungsschritt des Verringerns der Drehzahl der Hydraulikpumpe (8) oder des Hydraulikmotors (10), während das Arbeitsöl nicht von der Niederdruckleitung (14) zu einem Lager oder einer Dichtung von wenigstens einem von der Hydraulikpumpe (8) und dem Hydraulikmotor (10) zugeführt wird, nachdem der abnormale Stopp der Verstärkerpumpe (22) in dem Detektionsschritt detektiert wurde.
  12. Betriebssteuerungsverfahren für eine Windturbinen-Energieerzeugungsvorrichtung (1) nach Anspruch 11,
    wobei in dem Drehzahlverringerungsschritt eine Verdrängung sowohl der Hydraulikpumpe (8) als auch des Hydraulikmotors (10) auf einen Minimumwert eingestellt wird, während der Anstellwinkel des Windturbinenrotors (3) so gesteuert wird, dass eine aerodynamische Bremskraft auf den Windturbinenrotor (3) wirkt.
EP14188979.0A 2013-10-17 2014-10-15 Hydraulikgetriebe, Windturbinengenerator und Betriebssverfahren dafür Active EP2891795B1 (de)

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JP2013216088A JP2015078739A (ja) 2013-10-17 2013-10-17 油圧トランスミッション及びこれを備えた風力発電装置並びに風力発電装置の運転制御方法

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CN106870289B (zh) * 2017-03-28 2023-08-08 兰州理工大学 一种静液储能式液压传动型风力发电机组及控制方法
ES2934959T3 (es) 2018-06-22 2023-02-28 Vestas Wind Sys As Sistema de fluido para una turbina eólica

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DE4313025A1 (de) * 1993-04-21 1994-10-27 Zahnradfabrik Friedrichshafen Hydrostatisch-mechanisches Getriebe zum Antrieb einer Mischtrommel
WO2013021670A1 (ja) * 2011-08-10 2013-02-14 三菱重工業株式会社 再生エネルギー型発電装置

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